Mud pumps



y 1962 J. H. WILSON 3,033,124

MUD PUMPS File June 1956 8 Sheets-Sheet 1 cla INVENTOR John Hart WilsonWWW AGEN I J. H. WILSON May 8, 1962 MUD PUMPS 8 Sheets-Sheet 2 FiledJune 6, 1956 Fig.3

AGENT.

y 1962 J. H. WILSON 3,033,124

MUD PUMPS Filed June 6, 1956 8 Sheets-Sheet 3 INVENTOR John Hart Wilsony 8, 1962 J. H. WILSON 3,033,124

MUD PUMPS Filed June 9 8 Sheets-Sheet 4 Fig.5

f INVENTOR nag John Hart Wilson J. H. WILSON May 8, 1962 MUD PUMPS 8Sheets-Sheet 5 Filed June 6, 1956 INVENTOR John Han Wilson y 8, 1962 J.H. WILSON 3,033,124

MUD PUMPS Filed June 6, 1956 8 Sheets-Sheet 6 1N VEN TOR.

John Hart Wi Is on WsHW A GEN T.

y 8, 1962 J. H. WILSON 3,033,124

MUD PUMPS Filed June a, 1956 8 Sheets-Sheet a IN VEN TOR.

John Hart Wilson AGENT.

States 3,033,124 MUD PUMPS John Hart Wilson, R0. Box 329, Wichita Falls,Tex. Filed June 6, 1956, Ser. No. 589,752 4 Ciairns. (Cl. 103-416) Unitetofore, but these were usually of relatively heavy construction, and thebody parts of the pump were usually of heavy case construction;therefore, a pump of large pumping capacity was heavy and cumbersome inproportion to the amount of fluid handled.

The present pump is designed to include structural features which willresult in a pump which is relatively light in weight, yet theconstruction of which will equal or exceed in strength, a much heavierpump. The pump case is provided with openings both in the sides and topthereof which provide maximum accessibility into the packing chamber,both to the piston rod glands and to the pony rod glands, and also forthe removal of the piston rods.

The present pump is designed to be of such capacity as to handle avolume of fluid which will equal or exceed the amount of fluid handledby many pumps now in use, which are larger and heavier.

An object of this invention is to provide a mud pump which utilizesrigid, fabricated, plate metal case which is welded into an integralunit, so as to form the power end of the pump, the cylinders and valvechambers of which constitute the fluid end of the pump, and are of castmetal construction and are so designed as to enable the cylinders andvalve assemblies to be attachably bolted to the case in aligned relationtherewith.

Another object of the invention is to provide a crosshead bearing on theconnecting rod of the pump, whereby the load will equalize over theentire bearing, even if the connecting rod is slightly out of alignmentwith the axis of the pump.

Still another object of the invention is to provide a tongue and groovebearing mounting plate, for the crank shaft of the pump, whereby thecrankshaft, bearings, and associated parts may be installed in the pumpas a unit, and which may be readily removed therefrom as a unit.

Yet another object of the invention is to provide a case, for the powerend of a pump, which is of fabricated, plate and welded construction,whereby tension members are provided within the case to transmitreaction forces through the length of the pump case from the power endto the fluid end and yet maintain the hearings in aligned relation withrespect to the axis of the fluid end.

A further object of the invention is to provide a welded steel plateframe with a removable bearing cap over the main bearing housing, whichis held in place by fitted bolts in double shear, in such manner thatthe bearing cap is readily removable, and yet, when in place with thefitted bolts installed, has very great strength, with a minimum ofweight.

A still further object of the invention is to provide an oiling systemfor the pump mechanisms, whereby certain parts of the pump arelubricated by oil under pressure atet ice;

from an oil pump, and whereby certain other parts of the pump arelubricated by flooding the parts with oil.

With these objects in mind, and others which will become manifest as thedescription proceeds, reference is to be had to the accompanyingdrawings, in which like reference characters designate like parts in theseveral views thereof, in which:

FIG. 1 is a side elevational view of the mud pump assembly, with partsbroken away to show the interior construction thereof;

FIG. 2 is a fragmentary view showing a portion of the lubricatingsystem, with parts being removed, and other parts being shown in sectionto bring out the details of construction;

FIG. 3 is a view, greatly enlarged, taken approximately between thelines A-A of FIG. 1, a portion of the cover housing being broken away toshow the details of construction;

FIG. 4 is an enlarged, longitudinal, sectional view taken substantiallybetween the lines B-B of FIG. 1, to show the interior details ofconstruction of the pump;

FIG. 5 is an enlarged, longitudinal section, detail view, takensubstantially between the lines O-C of FIG. 1, having certain partsbroken away, and other parts shown in section to illustrate the detailsof construction;

FIG. 6 is a greatly enlarged, fragmentary detail, vertical sectionalview through one of the valve seats and the chamber thereof, and showingthe valve in full outline with an O-ring sealing element between thevalve seat and the valve housing;

FIG. 7 is an enlarged, longitudinal, sectional view of a portion of thepiston rod and a portion of the connecting rod, and showing a mud splashshield connected thereto;

FIG. 8 is a sectional view taken on the line 8-8 of FIG. 7, looking inthe direction indicated by the arrows;

FIG. 9 is an enlarged, transverse, sectional view taken through thecross-head, to show the details of construction;

FIG. 10' is a fragmentary view showing the end portion of a connectingrod and showing the crosshead assembly parts therein;

FIG. 11 is an enlarged, fragmentary elevational view of a crankshaftbearing housing;

FIG. 12 is a cross-sectional view taken on the line 12-42 of FIG. 1,looking in the direction indicated by the arrows; and with parts brokenaway and parts shown in elevation to bring out the details ofconstruction;

FIG. 13 is a fragmentary, perspective view of a portion of the pumpcase, with parts shown in exploded position to show the details ofconstruction;

FIG. 14 is a fragmentary, sectional view taken on the line 14--14 ofFIG. 13, looking in the direction indicated by the arrows, and showingthe laminated plates secured together by weld-rivet means;

FIG. 15 is a fragmentary longitudinal sectional view through a portionof the pump body, pump cylinder liner, and the packing gland arrangementtherebetween;

FIG. 16 is a longitudinal sectional view of the fabricated case of thepump, showing the internal, reactionary thrust or tension members, andshowing the oil pump driving sprockets and chain;

FIG. 17 is a sectional view taken on the line 1717 of FIG. 5, looking inthe direction indicated by the arrows;

FIG. 18 is an enlarged, fragmentary, longitudinal view of the cylinderhead and cylinder liner retaining unit;

FIG. 19 is a perspective view of a removable oil sump sediment pan,shown apart from the pump;

FIG. 20 is a perspective view of a lubricant strainer unit, shown apartfrom the pump;

FIG. 21 is an assembled, elevational view of the outermost lamination ofthe laminated plates that go to make 3 up the crank case housing for thepower end of the pump;

FIG. 22 is a sectional view taken on the line 22-22 of FIG. 21, lookingin the direction indicated by the arrows;

FIG. 23 is an assembled, elevational view of the center lamination ofthe laminated plates that go to make up the crank case housing of thepower end of the pump;

FIG. 24 is a sectional view taken on the line 24-24 of FIG. 23, lookingin the direction indicated by the arrows;

FIG. 25 is an assembled elevational view of the innermost lamination ofthe laminated plates which go to make up the crank case housing for thepower end of the pump;

FIG. 26 is a sectional view taken on the line 2626 of FIG. 25, lookingin the direction indicated by the arrows;

FIG. 27 is an elevational view of the composite of the outer, center,and inner laminations of the plates that go to make up the crankhousing; and

FIG. 28 is a sectional view taken on the line 28-28 of FIG. 27, showingthe manner of assembling the laminations to form the plates.

With more detailed reference to the drawings, the numeral 1 designates abase or skids, upon which a case, generally designated at 2, is mounted,as is the cylindervalve assembly, generally designated at 4. The case 2is of welded plate construction, as will best be seen in FIGS. 3, 4, 5,1O, 13, 14 and 16 through 18. The crank case 5 has a cover 6 attachablysecured thereto by means of wing bolts 8, as will best be seen in FIG.1.

The case 2 has a crankshaft 10 mounted transversely thereof withinbearings (FIG. 12). Connecting rods 12 and 14 are connected to thecrankshaft 10in a manner set forth in my co-pending application Ser. No.480,445, Crank Shaft Assembly, filed January 7, 1955, of which thisapplication is a continuation in part.

The crankshaft bearing assemblies 15 are mounted within the respectivebearing housings 16, as will best be seen in FIG. 12, one side of eachbearing housing engages a slide plate bearing cap assembly 18, so theentire crankshaft assembly may be readily removed, upon removal of theslide plates 18.

Attached to the respective throws of the crankshaft 10 are theconnecting rods 12 and 14, each of which connects with crossheads, asshown in FIGS. 4 and 9, which crossheads are designated by the numeral20. Each of the connecting rods 12 and 14 has a pair of annular bushings22 therein, the inner surface of each bushing being spherical and whichinterfits in complementary relation with an annular bearing 24, whichbearing 24 is preferably made of bearing bronze, and which has aspherical outer face. The annular bushings 22 are held in place byannular rings 26, which surround the bushings 22 and are bolted to therespective connecting rods 12 and 14, by means of cap screws 28.

An annular ring 30 surrounds the respective crosshead wrist pins 32, theends of which pins 32 are tapered. There is a slight clearance, usuallyabout .010", between the outer diameter of the annular ring 30 and theinner diameter of the annular ring 26. In this manner a limited rotarymovement, of the connecting rod and associated parts about itslongitudinal axis, with respect to the spherical bearing ring 24 andcrosshead wrist pins 32, is possible, so as to permit a limitedself-alignment of the respective parts. A cap member 34 is provided oneach side of each crosshead 20, so as to hold annular wedge rings 36 incontact with the taper 38 of the crosshead wrist pins 32 and with theinner diameter of the bore of the crossheads 20. The ring 34 is held inplace by means of bolts 40, as will best be seen in FIG. 9. Therespective crosshead wrist pins 32 are each drilled and cross drilled toprovide lubricant channels, which channels lead to grooves formed on theouter diameter of the wrist pins 32 in the respective crossheads 20. Alubrication connection 42 is screw threaded into an end of each wristpin 32, which lubrication connection is in communication with therespective passages 44 and 46 which lead to the longitudinal groovesformed in the top and bottom only of crosshead wrist pins 32.

A pony rod 48 is screw threaded into one end of each crosshead 20, aswill best be seen in FIG. 4. The threads engaging the respectivecrossheads are preferably tapered and each has a lock nut 50screw-threaded onto the respective pony rods 48, so as to abut with therespective crossheads 20 to securely hold the respective pony rods 48 inplace.

A piston rod 52 is screw-threaded into pony rod 48, which piston rod 52extends through gland 54 and connects with a piston 56, which is fittedwithin pump liner 58. A pump cylinder liner 58 is of the character asset forth in my co-pending application Ser. No. 454,082, filed Sept. 3,1954 for Cylinder Assembly, now Patent No. 2,832,653 dated April 29,1958.

The cylinder and valve assembly, the cast body of which is designatedgenerally at 4, is shown in elevation, with parts broken away, and withparts shown in section, in FIG. 5. Each cylinder and valve assembly body4 comprises a cylinder or cylindrical cavity 70 in which is mounted acylinder liner 58 and the outer end of which is closed by a disc-likecylinder head 64. A pump cylinder liner retainer member 60 bears againstthe outer end of each of the pump cylinder liners 58, the retainers 60being held in place by screw bolts 62 which pass through each cylinderhead 64 and engage bridging portions of the respective retainers 60, andwhich bolts 62 are held against rotation by the respective threaded nuts63. An annular ring 69 is secured to the end of the respective cylinderand valve assemblies 4 by means of bolts 71. Each annular ring 69receives a cylinder head 64 therethrough in abutting relation with theend of the respective cylinder and valve chamber assemblies 4. Eachannular ring 69 is internally screw threaded to threadably receive anexternally screw threaded annular sleeve member 66 an end face of whichabuts with a shoulder on cylinder head 64. An O-ring sealing element 68is interposed between the inner face of the respective cylinder heads 64and the end of the respective cylinder and valve chamber assemblies 4,and surrounds the respective cylinder 70 so as to form a fluid tightjoint between the cylinder heads 64 and the cylinder and valve chamberassemblies 4.

The cylinder liner retainer member 60 has a radially extending lug 61thereon at the outer end thereof (FIG. 18), which lug extends outwardlyand fits into a slot 64:: formed in the end of the cylinder head 64. Thecylinder heads will not seat properly unless the respective lugs 61 areinterfitted within the respective slots 64a, so as to maintain thecylinder retainer members in a fixed relation with respect to thecylinder heads 64. In this manner the liner retainer members will havethe openings thereof in register with the respective inlet and outletports leading to the respective inlet and outlet valves.

Each of the annular rings 69 has a groove or keyway 73 formedlongitudinally therein, which groove or keyway is adapted to receive akey 73a which is attached to the cylinder head 64 by means of a screw73b. In this manner, when the cylinder head 64 is in place, the lugs 61and the slots or grooves 64a are in register, and with the keys 73afitted within the respective grooves 73, the cylinder liner retainermembers 60 will be in the correct relation to the respective cylinders.

At the outer end of each cylinder 70, an O-ring 72 (FIG. 5) forms a sealbetween the respective pump liners 58 and the inner diameter of the boreof each cylinder 70. A packing is interposed between a stepped shoulderon each pump cylinder liner 58 and the stepped shoulder portion of theinternal bore of each cylinder 70 (FIG. 15). It is preferable to havetwo or more packing rings, as indicated at 74, between the steppedshoulder portions, with a ring 76 therebetween, which ring 76 hasexternal groove 78 and internal groove 80 formed therein, with the holes82 interconnecting the grooves 78 and 80. Pipes 84 and 86 arescrewthreaded into passages formed within the respective cylinders 70,so as to form an outlet for any fiuid that may leak past the sealingelements between the pump cylinder liners and the pump cylinders, whichpassages interconnect the respective outer grooves 78.

It is preferable to have the bore of the cylinder 70 slightly larger indiameter, for a portion of the length thereof, than the outside diameterof the pump cylinder liner 58, so that grease may be pumped through agrease fitting 88 into the annular space between the cylinder and thepump cylinder liner, under pressure, so as to normally prevent entranceof foreign matter, such as mud, sand or the like. A relief plug 88a isprovided at the top of cylinder 70 so as to vent air to enable thefilling of the annular space between the inner bore of the cylinder 70and the cylinder liner'SS. A connection 88b is provided in cylinder 70to enable a high pressure pump connection to be attached thereto toenable the removal of the cylinder liner, as set forth in my co-pendingpatent application Ser. No. 454,082, Cylinder Assembly.

The power end of the pump case is fabricated, and

.is so constructed as to give maximum strength at points where strengthis needed, thereby enabling the rest of the structure to be maintainedat a minimum of weight.

FIGS. 3, 4, 5, ll, 12, 13, 14, l6, l7 and 21 through 28 illustrate themanner of fabricating and assembling the power end of the pump case. Thepump case is provided with a bottom plate 90 and a top plate 92- and anintermediate, horizontal plate 94, and side plates 96. An end plate 97is provided, as will bestbe seen in FIGS. 5, l6 and 17. The respectiveplates 90, 92, 94, 96 and 97 are welded together in suchv manner as toform an integral uni-t. Plates 98 and 99 are also secured to side plates96, which, together with cover plate 6, form a housing for thecrankshaft 10, and sprockets 100 and 101 which drive the pump.

The side plates 96, as shown in FIGS. 13 and 16, are composed of amultiplicity of plate elements welded together in laminated relation, asshown in FIGS. 21 through 28.

One of the side plates, designated generally at 96 in FIG. 27, is acomposite of side plate elements 96a, 96b, 96c, 96d and 96e, 961, 96gand 96i. The side plate elements 96a through 96,0 comprise an outerplate element, which is divided along the lines a so the abuttingsurfaces a may be machined as by grinding or the like, in order toprovide a precision fit. The faces b and c are also machined, as bygrinding, before the assembly of the The side plate elements 96a, 96b,and 960 are beveled at the abutting joints a, so when the surfaces a, band 0 have been machined to a precision tolerance, the side plateelements 96a, 96b and 960 are fitted together, as shown in FIG. 1, andwelded at the beveled portions throughout the greater portion of theabutting length a until the weld is slightly above the surface of thebase metal, whereupon the surfaces of the plate are ground until the topof the weld is in the same plane as the finished face of the base metal.In this manner a precision fit may be had on all straight surfaces ofthe side plate elements 96a, 96b and 96p. The side plate elements 96a,96b and 960 are beveled on the near side as indicated at u, shown inFIG. 21, and are beveled on the far side as indicated at v, so as toenable the welding of the outer side plate elements to the center sideplate elements.

The side plate portions comprising the elements 96d 962 and 96 areground or machined along the surfaces d, e and f to within a closetolerance, therefore, when the surfaces are abutted, the unit will bewithin a close tolerance of the correct size. With the surfaces ofabutting, as shown in FIG. 23, and with the corners adjacent tht abuttededges beveled, as indicated in FIG. 24, the plate elements are weldedtogether, as indicated in FIG. 24, to form an integral plate, such asshown in FIG. 23. The grooves formed by the beveled portions of theelements are filled by Weld material, whereupon, both sur- 6 faces ofthe plate are finished, including the finishing of the weld, until bothsurfaces are parallel and within the correct plane tolerance.

As shown in FIG. 23, certain portions of the periphery of the centerplate elements are beveled, the bevel on the near side being indicatedat w and the bevel on the far side being indicated at x, which enablesthe plate elements to be welded together as shown in FIGS. 21 and 23.

The inner side plate elements, as shown in FIG. 25, comprise the threeelements 96g, 96h and 96i. A surface of side plate element 96g ismachined and abuts with machined or ground surface 9611 which abuttingsurfaces are indicated by the letter g. The corners of the adjacentabutting elements for a portion of the abutting surfaces are beveled toenable the welding of the two components together. Side element 96i ismachined or ground on one end thereof so as to abut with a machined orground surface 96h, so when these elements are fitted in abuttingrelation, they will be within the working tolerance required of theseparts. Corners on the elements 96h and 96i are beveled for a portion ofthe length of the abutting faces to enable the welding of the componentparts together when these elements 96g and 96i are welded to theelements 96h, the weld fills the groove for-med between adjacentabutting elements slightly above the surface of the base metal, so whenthese are welded together, the surface of the plate may be machined orground to a plane surface, so as to fit in side by side relation, asshown in FIG. 26. The peripheral edge is beveled at y on the near sideand at z on the far side.

With the outer, center and inner side plate elements assembled, as shownrespectively in FIGS. 21, 2.3, and 25, and with the inner surface of theouter side plate, as shown in FIG. 21, ground or finished in a planesurface, and with both sides of the center side plate element, as shownin FIG. 23, finished or ground into parallelplane surfaces, and with theouter face of the inner side plate element, as shown in FIG. 25, groundor finished to a plane surface, these side plates are placed insuperposed relation, so the axis of the arcuate surface k is cormnon toall three plates, with the plates occupying their respective positions,the plates are then clamped together in a jig, and welding performed onthe edges until the three side plate elements are welded into acomposite unit, such as shown in FIG. 27, ready to be assembled into thecrank housing of the power end of the pump. Whereupon, the unit is readyto be Welded, as shown in FIG. 27, at adjacent abutting edges of plates96j and longitudinal bar members 102, with the bars 102 abutting withside plates, as indicated at m and with the sides of the bars contactingadjacent surfaces n, whereupon, the bars are welded along the abuttingsurfaces In and n so as to transfer reaction force from the heavy platedirectly to plate 97 to which fluid cylinders are secured as by studs orthe like.

After the side plates are assembled into the casing, substantially asshown in FIG. 16, and with tongue and groove slide plates 18 bolted inplace, and with the outer, center and inner side plate elements studwelded together substantially in the manner shown in FIG. 14, at variouspoints throughout the plate area of the laminated plates, the pumpcasing is fitted on a boring mill in such manner that holes 96!: willaccommodate a bearing assembly, as shown in FIG. 12, and the hole 96lwill accommodate a counter-shaft assembly, as shown in FIG. 16.

After these laminated plate assemblies are machine-d, the slide plate 18 may be readily removed and replaced, and since the bolts are fitted tothe exact size of the hole, the bearing hole K in the slide plate willfit around the anti-friction bearing in the same relation as if the unitwere made of a solid plate of metal.

By having the notch formed at approximately a 45 degree angle withrespect to the horizontal, the slide plate 18 will slide in tongue andgroove relation in abutting relation to the bearing housing tapered ring16a, so as to hold the bearing in secure relation yet permit readyremoval of the bearing with the crank shaft asembly, when desired. Sincethe bearing is at an angle of about 45 degrees to the horizontal thecomponent of force exerted by the pump connecting rod transmits part ofthe force to the angular faces of the interfitting slide plate 18 andthe housing side plates 96 and part to the fitted bolts, there foregreater strength can be obtained than if the force was transmitteddirectly to tension bolts, furthermore, the tongue and grooveconstruction admits of using bolts in double shear, which enables astronger construction to be had, with the use of lighter weightmaterial.

Longitudinal tension members 102 are provided at each corner of the pumpcase and extend from end plate 97, to which the fluid end of the pump isbolted by bolts 103, to the opposite end of the pump case, and areWelded to the laminated side plates, in which the crankshaft bearingsare journaled, as will best be seen in FIGS. 16 and 27. Medialreinforcement tension bars 104, likewise extend between end plate 97 andtransverse bars 105 positioned along the top and bottom of the pumpcasing, as will best be seen in FIG. 16. A transverse bar 106 is securedadjacent the end plate 97 and is secured by welding to the end plate 97and top plate 92, as well as to longitudinal tension members 102 and104. Likewise, a transverse bar 107 is secured to intermediate plate 94,end plate 97 and longitudinal tension members 102 and 104 by welding, aswill best be seen in FIGS. 16 and 17. Vertical bars 106a are provided ineach corner adjacent end plate 97 and are welded to the side plates 96and end plate 97 and to the longitudinal tension members 102. Thisstrengthens end plate 97 against flexing and also strengthens the pumpcasing where strength is most needed. In this manner, the reaction forcebetween the crank and the piston, when pumping fluid, is transmittedthrough these tension members throughout the length of the case, and isdistributed across plate 97, to which the fluid end of the pump isbolted, thereby attaining maximum strength with a minimum of weight.

The pump case is provided with removable doors 108, 110 and 112 on eachside thereof, as well as with removable doors 111, 113 and 114 on thetop portion of the easing, thereby enabling ready access to theinterior, and the openings for which the doors are provided, tend tolighten the case, at points where great strength is not needed.

The pump in general, comprises three major units, namely, the skids 1,case 2, and the valve-cylinder assemblies 4. The case 2, as will best beseen in FIGS. 12, 13, and 14, is constructed of laminated steel platesaround the crankshaft bearing housings, and these plates welded tosingle thickness plates and to tension bars 102 and 104, which carry theload to the end plate 97, which bolts to the cylinder assembly. In thisway, the construction is so designed as to have the maximum strength atthe points of greatest strain, and to provide means for removing thebearing caps, so the crank assembly can be removed as a unit. Theselaminated plates are so ground and fitted and jig welded together as topresent a case wherein the crankshaft and anti-friction bearings may beremoved as a unit, by removing slide plate assemblies 18. The slideplate assembly is of a construction that interfits with complementarytongue and groove construction of the crank case 5, so when the partsare fitted together, a perfect bearing receptacle opening is formedtherethrough, and by inserting fitted bolts through the bolt holes inthe laminated plates, the bolts are placed in double shear by thereaction force of the crankshaft. Furthermore, as slide plate assembly18 interfits within the notched portion 96k of the respective sideplates 96, of the crank case, at an acute angle with respect to the lineof force of the connecting rod of the pump, so that the faces of theplates 18 and 96 will take a major component of the force set up by therespective connecting rods. Therefore, much greater strength may be hadby this construction than by a construction using single layer plates,or the common construction using tension bolts to bolt on the bearingcap.

Strainer units and 115a are provided, which are removably attached tothe exterior of the case, so as to enable the filtering of rodlubricating oil, and crankcase lubricating oil, respectively, whichpasses therethrough. The strainers are readily removable for cleaning orreplacement. A sludge pan 116 is provided, into which rod lubricatingoil passes, before it passes through strainer 115, thereby enabling theheavy sludge to settle out into the sludge pan, where it may be readilyremoved, before the lubricant is passed through the strainer 115a. Thestrainer 115a, which filters the crankcase oil, may be removed forcleaning when necessary. A filter unit 115b is connected within thecrankcase oil system for further cleaning of the crankcase oil.

Each of the cylinders 70, together with two suction valve pots 117, andtwo discharge valve pots 117a, are cast as an integral unit, and for aduplex pump, they are similar, except one is a right hand unit and theother is a left hand unit. An inlet pipe 118 has L-fittings 118a, whichare welded thereto and to the inlet of each of the inlet valve pots.Inlet valves 119 are fitted within the respective valve pots, so thatthe fluid or mud can be drawn therethrough into pump cylinder 70 andcylinder liner 58, upon reciprocation of the pump piston 56.

Discharge valve pots 117a each has a discharge valve 121 therein, whichdirects drilling fluid outward from cylinder 70 through tapered valveSeat 120, thence outward through discharge pipe 122a leading todischarge pipe 122. The valve seat is grooved, as shown in KG. 6, andhas an O-ring 120a therein which forms a seal with valve pot 117a. Boththe inlet and outlet valve seats are constructed in this manner.

The packing gland 54 has a threaded, cylindrical casing 124 therearound,which packing gland has gear teeth 126 thereon to mesh with a gear 128,which is mounted on one of the bolts 103, as will best be seen in FIG.17. The gear 128 has an axial hole therethrough, and is mounted on astud shaft 130, which shaft 130 is mounted on a cylinder head stud bolt103, immediately above the packing gland 54. A portion 132, on the endof gear 128, is of hexagon shape, so as to enable turning the gear, byengaging a wrench on the hexagon portion thereof, which in turn, willtighten or loosen cylindrical casing 124. A pipe 134 is provided forsupplying lubricant and coolant directly onto the piston rod 52, whichpipe 134 is connected with a suitable source of fluid supply.

Having thus described the invention, What is claimed is:

1. In a mud pump or the like, the combination of a body having acylindrical bore formed therein, said body having valve ports andpassages formed therein which valve ports and passages are in fluidcommunication with said cylindrical bore, a pump cylinder liner fittedwithin said cylindrical bore of said body, a pump cylinder linerretainer fitted within said bore and having one end thereof in bearingrelation with an end of said pump cylinder liner, the other end of saidpump cylinder liner retainer having a bridging portion thereon, anannular ring having an opening therein larger than the diameter of saidbore in said body and adapted to seat on an end of said body and beingaxially aligned with the bore thereof, bolt means bindingly securingsaid annular ring to said body, a disc-like cylinder head, the diameterof which is greater than the diameter of said cylindrical bore of saidbody and of less diameter than the opening in said annular ring, fittedagainst said body so as to substantially close the end of said bore, acompressible sealing element interposed between said pump body and saiddisc-like cylinder head so as to form a fluid tight seal between saidbody and said disc-like cylinder head, said cylinder head having athreaded aperture therethrough, cylinder head retaining means attachablyfitted within said annular ring and being adapted to hold said disc-likecylinder head Within said annular ring and in binding engagement withsaid body, and screw threaded means engaging said threaded aperture insaid disc-like cylinder head and abutting the bridging portion of saidpump cylinder liner retainer so as to bindingly engage said pumpcylinder liner retainer with said pump cylinder liner.

2. A mud pump as defined in claim 1, wherein said portion of saiddisc-like cylinder head which abuts with said body is beveled, andwherein said body has a complementary bevel formed thereon.

3. A mud pump as defined in claim 1, wherein said annular ring isinternally threaded, and wherein said cylinder head retaining means isexternally threaded to engage said threads of said annular ring.

4. A mud pump as defined in claim 1, wherein at least one of saidinterengaging elements has a groove formed therein, and wherein saidcompressible sealing element is fitted within said annular groove so asto be interposed between said pump body and said disc-like cylinderhead.

References Cited in the file of this patent UNITED STATES PATENTS

